Adjustable damping valve arrangement

ABSTRACT

An adjustable damping valve arrangement for a vibration damper comprises an actuator which exerts an actuating force on an auxiliary valve body of an auxiliary valve. The auxiliary valve influences a closing force on a main stage valve. A pressure depending on the pressure level in a working space of the vibration damper acts on at least one pressure-impinged closing surface of the main stage valve via a flow connection. The flow connection is carried out so as to be functionally parallel to an incident flow of the main stage valve, and a flow-in opening of the flow connection is oriented at an angle of at least 60° to the flow direction into the main stage valve so that only a static pressure acts on the closing surface of the main stage valve.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention is directed to an adjustable damping valvearrangement for a vibration damper.

2. Background of the Invention

U.S. 2011/0168935 A1 relates to a generic adjustable damping valvearrangement in which its main stage valve body has two pressure-impingedsurfaces acting in closing direction. Among the advantages offered bythis type of construction of the main stage valve is that theconstruction of the opening surface in rebound direction is simplifiedas a result of the enlarged closing surface. As a result of this type ofconstruction of the damping valve arrangement, the damping force thatcan be achieved in compression direction is increased. This increase indamping forces can certainly be desirable, e.g., when a larger dampingforce range must be covered at a given actuator force.

However, there is also a demand for damping force characteristics whichare as soft as possible. Of course, in this case recourse could be hadagain to a constructional form with only one pressure-impinged surfacein closing direction at the main stage valve body. However, this optionis not expedient from a cost perspective.

It is thus an object of the present invention to make it possible todecrease the damping force level in a generic damping valve arrangement.

SUMMARY OF THE INVENTION

According to the invention, this object is met in that the flowconnection is carried out so as to be functionally parallel to anincident flow of the main stage valve, wherein a flow-in opening of theflow connection is oriented at an angle of at least 60° to the flowdirection into the main stage valve so that only a static pressure actson the closing surface of the main stage valve.

A reduced pressure on the pressure-impinged closing surface can beachieved by a simple guiding of flow inside the damping valvearrangement. An angle of 90° is preferably used.

To improve the effect of the pressure reduction, a deflecting profile isarranged upstream of the flow-in opening in flow direction.

In a further advantageous embodiment, the deflecting profile is executedon an annular element of the damping valve arrangement. Optionally, theannular element can be executed in the damping valve arrangement, i.e.,appreciably different damping force characteristic ranges can be coveredby a damping valve arrangement which is identical per se.

According to an advantageous embodiment, the annular element has channelportions of the flow connection. This simplifies production efforts forthe flow connection inside the damping valve arrangement.

A collecting channel running in circumferential direction is arrangeddownstream of the flow-in opening and is connected to individualchannels of the flow connection so as to allow any installation positionfor the annular element.

When two pressure-impinged closing surfaces are provided at the mainstage valve, for example, a closing surface can also be connected to theincident flow opening for an incident flow direction. However, there isalso the advantageous option of connecting a plurality ofpressure-impinged closing surfaces to the incident flow opening. Thelarger the pressure-impinged surface or surfaces, the greater theachievable effect for the reduction of damping force.

At least two pressure-impinged closing surfaces can also be arranged inseries with respect to the flow path. This type of construction leads tothe advantage that both pressure-impinged closing surfaces areinfluenced by one incident flow opening.

A particularly large difference in damping force between damping duringa compression movement and damping for a rebound movement is achievedwhen a flow-in opening is formed for only one working space.

In an alternative embodiment, a throttle is arranged in the flowconnection. For example, the throttle can be constructed in a sleevewhich can be pressed into the flow connection.

Other objects and features of the present invention will become apparentfrom the following detailed description considered in conjunction withthe accompanying drawings. It is to be understood, however, that thedrawings are designed solely for purposes of illustration and not as adefinition of the limits of the invention, for which reference should bemade to the appended claims. It should be further understood that thedrawings are not necessarily drawn to scale and that, unless otherwiseindicated, they are merely intended to conceptually illustrate thestructures and procedures described herein.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention will be described more fully below with reference to thedrawings in which:

FIG. 1 shows an adjustable damping valve arrangement with an incidentflow opening;

FIG. 2 shows adjustable damping valve arrangement with twopressure-impinged surfaces arranged in series; and

FIG. 3 shows an auxiliary valve body as individual part.

DETAILED DESCRIPTION OF THE PRESENTLY PREFERRED EMBODIMENTS

FIG. 1 shows a damping valve arrangement 1 which is fastened, e.g., to apiston rod 3 of a vibration damper, shown only partially. The dampingvalve arrangement 1 comprises a piston 5 which divides a cylinder 7 intoa working chamber 9 on the piston rod side and a working chamber 11remote of the piston rod, both of which working chambers 9; 11 arefilled with damping medium. In this embodiment example, the dampingvalve arrangement is fastened to the piston rod 3, but the invention isnot limited to an arrangement of this kind.

An actuator 15 of optional design is arranged in an outer housing 13.Serving as actuator in this example is a magnetic coil 17 which exerts aforce on an axially movable armature 19, this force being transmitted toa multiple-part auxiliary valve body 21 of an auxiliary valve 23. Thedesign of the auxiliary valve body is described in detail in connectionwith FIG. 3. At least one valve spring—in this variant, two opposingvalve springs 25; 27 are used—preloads the auxiliary valve body 21 inthe lift direction with respect to an auxiliary valve surface 29 of theauxiliary valve 23. The actuator 15 acts in the closing direction of theauxiliary valve 23. The force of the at least one valve spring 25; 27and the force of the actuator 15 form a resultant force which acts onthe auxiliary valve body 21 in the lift direction.

An auxiliary valve closing spring 30 impinges on an auxiliary valve seatbody 32 in closing direction regardless of the actuator setting.

A stepped opening 33 in which a main stage valve body 35 of a main stagevalve 37 can execute an axial movement is formed in an inner housing 31of the damping valve arrangement 1. The main stage valve body 35 has aguide sleeve 39 whose back side 41 forms a surface A_(SchlieβD) that ispressure-impinged by damping medium. Further, the main stage valve body35 has a radial shoulder 43 which has an additional pressure-impingedsurface A_(SchlieβD2) in the direction of the back side 41.

In a neutral position of the piston rod 3, i.e., without opening force,the main stage valve body 35 contacts a valve seat surface 45 of anaxially movable valve ring 47 which contacts a housing-side valve seatsurface 49 at the side of the axially movable valve ring 47 facing indirection of the working chamber 11 remote of the piston rod.

The main stage valve body 35 is formed of a plurality of parts. An outercup 51 forms the guide sleeve 39 and the radial shoulder 43. In aseparation plane, an inner disk 53 defines with the cup 51 a radialdamping medium flow path 55 between the additional pressure-impingedsurface A_(SchlieβD2), as part of the main stage valve, and a controlspace 57, as part of the auxiliary valve, whose outlet cross section isdetermined in direction of a rear space 59 by the valve body 21.

The additional surface A_(SchlieβD2) of the main stage valve body 35 canbe acted upon with damping medium via at least two flow paths. A firstfeed flow channel 61 is formed directly in the main stage valve body 35as an axial passage. An out-flow channel 63 extends inside the mainstage valve body 35 between the rear space 59 of the main stage valve 37and the damping medium flow path 55.

A flow connection 65 of the rear space 59 to the working chamber 11remote of the piston rod inside a connection sleeve 66 between the outerhousing 13 and the piston 5 is controlled by an emergency operationvalve 67. The emergency operation valve 67 is formed by a valve ring 69which is lifted from an emergency operation valve seat surface 73 by theactuator 15 against the force of at least one closing spring 71. Even aslight application of energy is sufficient for the actuator 15 toachieve the lift movement of the valve ring 69. The auxiliary valveclosing spring 30 is also supported axially at the valve ring 69 so thatthere is a slight closing force of the auxiliary valve closing spring 30when the emergency operation valve 67 is open. In this example, themagnetic force of the magnetic coil 17 acts on the valve ring 69. As aresult of apt dimensioning of the spring forces and magnetic forces, astrict separation can be achieved between an emergency operating stateand a normal operating state. In this way, the flow path between therear space 59 and the working chamber 11 remote of the piston rod can beinfluenced by means of the emergency operation valve 67.

At least one connection orifice 75 leading from the working chamber 9 onthe piston rod side to the pressure-impinged surface A_(ÖZ) at theunderside of the radial shoulder and to the control space 57 is formedin the connection sleeve 66 of the damping valve arrangement 1. For thispurpose, the main stage valve body 35 has at least one axial opening 77in the region of the radial shoulder 43.

With the damping medium flow path 55 and the feed flow channel 61 fortwo separate incident flow paths A_(ÖZ) and A_(ÖD), the auxiliary valvealso has separate flow connection portions to the control space 57. Acheck valve 79 and a damping valve 81 functioning as a check valve arearranged in the feed flow channel 61 and in the flow-off channel 63 sothat damping medium does not escape through the feed flow channel 61 andflow-off channel 63 in the main stage valve body 35 in direction of theworking space 11 remote of the piston rod when there is an incident flowvia the connection orifice 75. In so doing, the damping valve 81 isconnected to the rear space 59 by the flow-off channel 63. During a liftmovement of the main stage valve body when the rear space is closed, thedamping valve 81 releases the flow path for a flow of damping medium outof the rear space 59 in direction of the additional surfaceA_(SchlieβD2) in connection with a damping force.

FIG. 3 is limited to a section from FIG. 1. The auxiliary valve body 21comprises a shaft portion 83 which forms an interference fit with thearmature 19. The shaft portion 83 is constructed as a hollow body inorder to supply a back side of the armature 19 with damping medium forhydraulic pressure compensation.

The shaft portion 83 is adjoined by a spring holder 85 which carries aspring element 87. The spring holder 85 has a guide pin 89 in thedirection of the shaft portion 83, which guide pin 89 engages in aradial positive-engagement connection with a guide surface 91 of theshaft portion 83.

The guide pin 89 has a fastening flange 93 for the spring element 87.The spring element 87, which is constructed as a disk spring, iscentered together with the auxiliary valve seat body 32 by a radial wall95 as part of the fastening flange 93. The spring element 87 acts upontwo portions of the auxiliary valve body 21 at a distance, namely theauxiliary valve seat body 32 and the shaft portion 83. The spring holder85 contacts the shaft portion 83 axially without clearance after thefinal assembly of the damping valve arrangement 1.

The spring holder 85 has a free space 97 for receiving a spring path ofthe spring element 87. For this purpose, the fastening flange 93 isconstructed with a cone. The disk spring 87 is supported by its outerdiameter at the cone. The cone forms a supporting surface 99 forlimiting the deformation of the spring element 87.

The wall 95 of the fastening flange 93 is constructed so as to besomewhat longer axially than the structural height of the disk spring 87and of the auxiliary valve seat body 32. A protruding portion serves fora positive-engagement connection so that the spring holder 85, thespring element 87 and the auxiliary valve seat body 32 form aconstructional unit.

The auxiliary valve seat body 32 is constructed as a solid component andhas a closure region 101 projecting into the control space 57 (FIG. 1).It adjoins a disk body 103 which extends radially up to the wall 95 ofthe spring holder 85. A central contact face is formed for the springelement 87 on the top side of the auxiliary valve seat body 32 facing indirection of the spring holder 85. Adjoining radially outwardly is aconical transition 105 which likewise receives the deformation path ofthe disk spring 87.

FIG. 1 further shows that a clamping pin 107 of the main stage valvebody 35 preloads at least one valve disk 109 of the damping valve 81 atleast indirectly in closing direction. Formed at the clamping pin 107 isa circumferential collar 111 which preloads at least one flexible valvedisk 109 of the damping valve 81 on a valve seat surface. The preloadingof a check valve spring 113 does not depend on the preloading of theflexible valve disk 109. The clamping pin 107 can be secured by aninterference fit in the main stage valve body 35. The loading capacityof the interference fit is appreciably greater than the preloading forceon the damping valve 81. Alternatively, a preloading spring 115 can bearranged axially between the clamping pin 107 and the inner disk 53 ofthe main stage valve body 35. The preloading force of the preloadingspring 115 is likewise greater than the required preloading force on thedamping valve 81.

There are four basic operating states to be considered which will bedescribed with reference to FIG. 1. A first operating state of thedamping valve arrangement 1 is characterized by an incident flowproceeding from the working chamber 11 remote of the piston rod via apassage 117 to the valve ring 47 and main stage valve body 35 in orderto lift the valve ring 47 and the main stage valve body 35 jointly inopening direction. Via passage 117, the damping medium flows mostly tothe main stage valve body 35. A volume flow controlling the function ofthe main stage valve 37 flows in the direction of at least one flow-inopening 119 of the flow connection 65. The flow-in opening 119 isoriented at an angle of at least 60° to the flow direction to the mainstage valve 37 and is arranged at an appreciable distance upstreamthereof with respect to the flow path to the main stage valve 37. Inthis concrete embodiment, the angle is virtually 90°. Consequently, onlya static pressure acts upon the closing surfaces A_(SchlieβD);A_(SchlieβD2) of the main stage valve 37. A deflecting profile 121 isarranged in front of the flow-in opening 119 in the flow direction. Thedeflecting profile 121 and the flow-in opening 119 are constructed on anannular element 123. Use of this annular element 123 is optional. Thisaffords the possibility of covering two distinctly different dampingforce characteristic ranges with an otherwise identical damping valvearrangement 1. The pressure level on the closing surfaces of the mainstage valve body is reduced by the annular element 123 with the resultthat the damping force characteristic tends to be softer. Alternatively,by dispensing with the annular element 123, both the static and dynamicpressure inside the damping valve arrangement can be made use of so thatthe pressure which is increased in comparison also has a greaterhydraulic closing force and, therefore, there is also a harder dampingforce characteristic of the damping valve arrangement 1.

Downstream of the flow-in opening 119, the annular element 123 has aradial channel portion 125 which forms part of the flow connection 65.Further, a collecting channel 127 which extends in circumferentialdirection and is connected to individual channels of the flow connection65 is arranged downstream of the at least one flow-in opening 119.

In this embodiment form, the flow-in opening 119 is effective only forthe pressure-impinged closing surface A_(SchlieβD). The additionalpressure-impinged surface A_(SchlieβD2) is supplied directly via thefeed flow channel 61 with damping medium under static and dynamicpressure.

Further, the use of the flow-in opening 119 oriented according to theinvention is realized only for the incident flow from the working space11 remote of the piston rod.

The emergency operation valve 67 is switched on, i.e., lifted from itsemergency operation valve seat surface 73 as in the illustratedposition, and the actuator 15 acts against the force of the valvesprings 25; 27. The preloading of the auxiliary valve closing springtakes on the minimum magnitude so that the valve closing spring haspractically no effect on the normal operating function of the dampingvalve arrangement. The damping medium flows along the first feed flowchannel 61 in the valve body 35 and the opened check valve 79, thenfurther along the damping medium flow path 55 to the additional valveclosing surface A_(SchlieβD2). A first closing force component exertsthe pressure on this valve closing surface A_(SchlieβD2). Further,damping medium flows through the flow connection 65 in the connectionsleeve 66 and through the opened emergency operation valve 67 into therear space 59. The damping valve 81 for the additional pressure-impingedsurface A_(SchlieβD2) is closed owing to the incident flow through thefeed flow channel 61. As was already described, the back side 41 of themain stage valve body 35 forms the pressure-impinged surfaceA_(SchlieβD) that is acted upon by the static pressure in the workingspace 11. The closing force acting on the main stage valve body 35 iscomposed of the resulting closing force, which acts directly on the backside 41 of the main stage valve body 35 via the auxiliary valve body,and the pressure forces on surfaces A_(SchlieβD) and A_(SchlieβD2). Asurface A_(ÖD) at the valve ring 47 is slightly larger than the sum ofsurfaces A_(SchlieβD) and A_(SchlieβD2) so as to exclude blocking of thelift movement of the main stage valve body 35 due to the pressureratios. The pressure in the control space 57 of the main stage valvebody plays no part in this incident flow direction of the damping valvearrangement because the auxiliary valve is bypassed by the flowconnection 65 to the rear space 59.

Particular with minimal energizing of the actuator 15 and with anincident flow of the main stage valve body 35, the auxiliary valve seatbody 32 can quickly move slightly to the shaft portion 82 against thesmall closing force of the spring element 87. The main stage valve body35 can follow this movement and take up a passage. The inertia of thearmature 19 in this case does not affect this initial movement of themain stage valve body 35 because the spring element 87 functions in aseries connection with the armature 19. When the relative movement ofthe auxiliary valve seat body 32 toward the shaft portion 83 isconcluded as intended by operation, the spring element 87 contacts thespring holder 85.

A second operating state concerns the emergency operating state of thedamping valve arrangement 1 and an incident flow of the damping valvearrangement 1 proceeding from passage 117. The emergency operation valve67 is closed due to the absence of energy supply via the actuator 15.The auxiliary valve seat body 32, as part of the auxiliary valve body21, is guided so as to be slightly displaceable axially inside theauxiliary valve body 21. In the deenergized state of the magnetic coil17, the valve springs 25; 27 hold the shaft portion 83 of the auxiliaryvalve body 21, considered statically, i.e., without incident hydraulicflow, at a maximum distance from the auxiliary valve seat surface 29.Therefore, the auxiliary valve seat body 32 could occupy a maximum liftposition when loaded even by the slightest pressure proceeding from thecontrol space 57. When the emergency operation valve is closed, however,the preloading of the auxiliary valve closing spring 30 is maximized.Regardless of the dimensioning of the valve springs 25; 27, theauxiliary valve closing spring 30 moves the auxiliary valve seat body 32into a closed position on the auxiliary valve surface 29. The rear space59 is accordingly closed off from any incident flow via the controlspace 57 and flow connection 65. As in the normal operating state, thedamping medium reaches the additional pressure-impinged surfaceA_(SchlieβD2) via the feed flow channel 61 in the main stage valve body35 and the open check valve 79. In order that the main stage valve body35 together with the valve ring 47 can lift from the housing-side valveseat surface 49, the damping valve 81 in the main stage valve body 35opens so that damping medium which is displaced from the rear space 59can flow off via the flow-off channel 63 in main stage valve body 35 indirection of the additional pressure-impinged surface A_(SchlieβD2).Accordingly, the main stage valve cannot open quickly in an uncontrolledmanner, but only after overcoming the damping force of the damping valve81. When the motion of the piston rod is reversed, the opening pressureon the main stage valve body 35 decreases and a closing spring 129 movesthe main stage valve body quickly back into the closed position withopen check valve 79.

The third operating state concerns an incident flow of the damping valvearrangement 1 proceeding from the working chamber 9 on the piston rodside and open emergency operation valve 67. The damping medium flowsthrough the connection orifice 75 in the connection sleeve 66 to thepressure-impinged surface A_(ÖZ) at the radial shoulder 43 and then tothe pressure-impinged surface which now functionally forms a closingsurface A_(SchlieβZ). The pressure-impinged surface at the radialshoulder of the main stage valve body is operative for both incidentflow directions of the damping valve arrangement. Depending on theenergy supply of the actuator 15, there ensues an auxiliary valveposition by which, in turn, a control pressure in the control space 57and accordingly also at the pressure-impinged surface A_(SchlieβZ) canbe controlled. The pressure acting on an annular surface A_(ÖZ) opposesthe pressure acting in the closing direction on surface A_(SchlieβZ).Because of the outlet throttle 86 which now functions as an inletthrottle, there is a pressure gradient between the pressures at surfacesA_(ÖZ) and A_(SchlieβZ) when the auxiliary valve 23 is open, so that thehydraulic opening force at the main stage valve body 35 is alwayssomewhat greater than the hydraulic closing force. The pressure in theconnection orifice 75 also acts on the valve ring 47 which isaccordingly pressed on the housing-side valve seat surface 49.Therefore, the main stage valve body 35 lifts from the valve seatsurface 45 of the valve ring 47. With its check valve function, thedamping valve 81 prevents a hydraulic short circuit of the auxiliaryvalve 23. The function of the spring holder 85 is identical to thatdescribed in the first operating state.

The damping medium flowing out of the control space 57 through theauxiliary valve 23 arrives in the rear space 59 and through the openemergency operation valve 67 and flow connection 65 in the connectionsleeve 66 into the working chamber 11 remote of the piston rod.Consequently, the rear space 59 has an inlet and an outlet with theworking chamber 11 of the vibration damper.

In the fourth operating state, the feed flow again takes place via theconnection orifice 75 in the connection sleeve 66, but the emergencyoperation valve 67 is closed. The flow path to the auxiliary valve 23corresponds to the description of the third operating state. Incontrast, the auxiliary valve 23 is closed due to the auxiliary valveseat spring 30. The closing spring 129 ensures that the main stage valvebody 35, together with the valve ring 47, is seated on the housing-sidevalve seat surface 49. This prevents a hydraulic short circuitingbetween the working chambers via the connection orifice 75. The dampingmedium arrives in the rear space 59 whose outlet is blocked by theclosed emergency operation valve 67. The damping valve 81 also remainsclosed. A flow path 131 to a pressure limiting valve 133 by which adefined pressure level in the rear space 59 can be determined is formedin the valve ring 69 of the emergency operation valve 67. The pressurelevel in the rear space 59 and, therefore, on the back side 41 of themain stage valve body 35 and on the pressure-impinged surface at theradial shoulder A_(SchlieβZ) determines the closing force in emergencyoperation of the damping valve arrangement 1. It is clear from acomparison of the second operating state and fourth operating state thatthe emergency operation valve 67 is effective in only one incident flowdirection of the damping valve arrangement 1 via the connection orifice75. Tests have shown that this design of the damping valve arrangement 1is suitable for reliable operating behavior of a vibration damper.

FIG. 2 shows a modification, based on FIG. 1, in which the twopressure-impinged closing surfaces A_(SchlieβD); A_(SchlieβD2) arearranged in series with respect to the flow path proceeding from theworking space 11 remote of the piston rod via the flow connection 65.There is no direct incident flow from the working space remote of thepiston rod via the feed flow opening 61 as in FIG. 1. Accordingly, it isalways only the static pressure that acts on both pressure-impingedclosing surfaces during an incident flow from the working space remoteof the piston rod.

Alternatively or in addition to the annular element 123, the flowconnection to the two pressure-impinged closing surfaces A_(SchlieβD);A_(SchlieβD2) can have a throttle 135 which once again reduces thepressure level proceeding from the static pressure in the working spaceremote of the piston rod. The functional difference between the throttle135 and the flow-in opening 119 consists in that the flow-in opening isalso effective when there is no flow connection between the workingspace and the pressure-impinged surface, but rather a stationaryconnection as is the case, e.g., when the emergency operation valve 67is closed.

Thus, while there have shown and described and pointed out fundamentalnovel features of the invention as applied to a preferred embodimentthereof, it will be understood that various omissions and substitutionsand changes in the form and details of the devices illustrated, and intheir operation, may be made by those skilled in the art withoutdeparting from the spirit of the invention. For example, it is expresslyintended that all combinations of those elements and/or method stepswhich perform substantially the same function in substantially the sameway to achieve the same results are within the scope of the invention.Moreover, it should be recognized that structures and/or elements and/ormethod steps shown and/or described in connection with any disclosedform or embodiment of the invention may be incorporated in any otherdisclosed or described or suggested form or embodiment as a generalmatter of design choice. It is the intention, therefore, to be limitedonly as indicated by the scope of the claims appended hereto.

We claim:
 1. An adjustable damping valve arrangement for a vibrationdamper comprising: an actuator (15); an auxiliary valve (23) comprisingan auxiliary valve body (21) and a main stage valve (37) having a flowdirection of a damping medium into said main stage valve and at leastone pressure-impinged closing surface; said actuator (15) exerting anactuating force on said auxiliary valve body (21) of said auxiliaryvalve (23) and said auxiliary valve influencing a closing force on saidmain stage valve (37); and a flow connection (65) for permitting apressure depending on the pressure level in a working space (9, 10) ofsaid vibration damper to act on at least one of said pressure-impingedclosing surfaces of said main stage valve (37); said flow connection(65) constructed so as to be functionally parallel to an incident flowof said main stage valve (37) and comprising a flow-in opening (119)oriented at an angle of at least 60° to the flow direction into saidmain stage valve (37) so that only a static pressure acts on said atleast one closing surface of said main stage valve (37).
 2. The dampingvalve arrangement according to claim 1, additionally comprising adeflecting profile (121) arranged upstream of said flow-in opening (119)in flow direction.
 3. The damping valve arrangement according to claim2, wherein said the deflecting profile (121) is an annular element (123)of said damping valve arrangement.
 4. The damping valve arrangementaccording to claim 3, wherein said the annular element (123) compriseschannel portions (125) of said flow connection (65).
 5. The dampingvalve arrangement according to claim 1, wherein said the flow-in opening(119) is arranged upstream of said main stage valve (37) with respect tothe flow path.
 6. The damping valve arrangement according to claim 1,additionally comprising a collecting channel (125) running incircumferential direction arranged downstream of said flow-in opening(119) and connected to individual channels of said flow connection (65).7. The damping valve arrangement according to claim 1, wherein said themain stage valve (37) comprises a plurality of pressure-impinged closingsurfaces for one incident flow direction which are connected to saidflow-in opening (119).
 8. The damping valve arrangement according toclaim 7, wherein at least two pressure-impinged closing surfaces arearranged in series with respect to the flow path.
 9. The damping valvearrangement according to claim 7, wherein a flow-in opening (119) isformed for only one working space (11).
 10. The damping valvearrangement according to claim 1, additionally comprising a throttle(135) arranged in the flow connection.